CN111022408A - Combination valve with return oil way compensation load sensing function - Google Patents
Combination valve with return oil way compensation load sensing function Download PDFInfo
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- CN111022408A CN111022408A CN202010008503.9A CN202010008503A CN111022408A CN 111022408 A CN111022408 A CN 111022408A CN 202010008503 A CN202010008503 A CN 202010008503A CN 111022408 A CN111022408 A CN 111022408A
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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Abstract
本发明公开了一种具有回油路补偿负载敏感功能的组合阀，包括多联阀组、供给油路P、回油路T、负载敏感油路LS，多联阀组公用统一的供给油路P、回油路T以及负载敏感油路LS，每联阀组均具有相同的元器件和装置组成以及相同的结构连接关系，第一联阀组包括一联第一二位二通比例阀、一联第二二位二通比例阀、一联第一二位二通电液动比例阀、一联第二二位二通电液动比例阀、一联压力补偿阀和一联控制油路。本发明通过进出口独立控制技术对负载敏感系统回油路压力的调节，使系统具备负载敏感功能的节能特性，解决了负载敏感系统中流量饱和状态下多执行器工作不同步的问题，减少了回油路通过阀口的节流损失，增强了系统执行器运行的平稳性。
The invention discloses a combined valve with the function of compensating the load sensitivity of the return oil circuit, which comprises a multi-connected valve group, a supply oil circuit P, an oil return circuit T, a load-sensitive oil circuit LS, and the multi-connected valve group shares a unified supply oil circuit P, return oil circuit T and load sensitive oil circuit LS, each valve group has the same components and device composition and the same structural connection relationship, the first valve group includes a first two-position two-way proportional valve, One-connected second two-position two-way proportional valve, one-connected first two-position two-way electro-hydraulic proportional valve, one-connected second two-position two-way electro-hydraulic proportional valve, one-connected pressure compensation valve and one-connected control oil circuit. The invention adjusts the pressure of the return oil circuit of the load-sensitive system through the independent control technology of the inlet and outlet, so that the system has the energy-saving characteristics of the load-sensitive function, solves the problem of asynchronous operation of multiple actuators in the flow-saturated state in the load-sensitive system, and reduces the problem of The throttling loss of the oil return circuit through the valve port enhances the smooth operation of the system actuator.
Description
Technical Field
The invention relates to a combined valve with independently controlled inlet and outlet oil paths, in particular to a combined valve with an oil return path compensation load sensing function, wherein the inlet and outlet oil paths can be independently controlled.
Background
The hydraulic transmission and control technology is one of the key technologies of transmission and control in the 4.0 era of the current industry, and great attention is paid to the hydraulic transmission and control technology in all countries in the world. The hydraulic system has the characteristics of high power density, compact structure, good controllability and strong environmental adaptability, but the defects of large installed power, low energy utilization rate, and common problems of too fast descending of the actuator under the action of gravity, air suction, large influence of load size on the working speed of the actuator, asynchronous operation of multiple actuators in a flow saturation state and the like.
The load-sensitive system is a hydraulic circuit which only provides the required flow and pressure according to the pressure and flow requirements of the system, and can greatly reduce energy waste caused by overhigh power of the hydraulic pump. The load sensitive system needs a variable plunger pump and a pressure compensation valve, when the pressure compensation valve is positioned on an oil return path, the system is called as an oil return path compensation load sensitive system, the problems that multiple actuators work asynchronously and the actuator with small load moves first in a flow saturation state can be solved, but the traditional proportional reversing valve simultaneously controls an inlet oil path and an outlet oil path of the actuator by utilizing a multi-edge throttling main control valve core, and an oil outlet valve port throttles simultaneously when an oil inlet valve port of the proportional reversing valve throttles, so that repeated throttling loss is caused, the energy consumption of the system is increased, and the efficiency is reduced.
The inlet and outlet independent adjustment is a novel valve group technology with the inlet and outlet throttle areas capable of being independently controlled, the technology can solve the problem of energy loss caused by simultaneous throttling of an oil inlet throttle edge and an oil return throttle edge in the one-way working process of the valve core, can realize different meso-position functions, and can realize different actuator working effects and energy-saving effects by adopting a specific control strategy according to specific working conditions and actuators. However, the technology has the problem that the multiple actuators work asynchronously under the flow saturation state.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a combination valve with an oil return path compensation load sensitivity function, which not only has the energy-saving characteristic of the load sensitivity function, but also has simple structure, good interchangeability and higher efficiency and economic benefit, solves the problem that a plurality of actuators work asynchronously in a load sensitivity system under the flow saturation state, reduces the energy waste caused by throttling of oil inlets and oil outlets of a proportional reversing valve at the same time, and improves the energy utilization rate of a hydraulic system; the pressure of an oil return path of the load sensitive system is regulated by an inlet and outlet independent control technology, and the running stability of a system actuator is enhanced.
In order to solve the technical problems, the invention adopts a technical scheme that: the utility model provides a combination valve with sensitive function of return circuit compensation load, including the group valve that ally oneself with more, supply with oil circuit P, return circuit T, the sensitive oil circuit LS of load, the public unified oil circuit P, return circuit T and the sensitive oil circuit LS of supplying with of the group valve that ally oneself with more, each ally oneself with the group valve and all have output oil port An, output oil port Bn that link to each other with the executor, its characterized in that: the multi-connection valve group comprises a first connection valve group, a second connection valve group, a third connection valve group and … …, wherein N is a natural number more than or equal to 1;
each valve group has the same components and device composition and the same structural connection relationship;
the first valve bank comprises a first two-position two-way proportional valve, a second two-position two-way proportional valve, a first two-position two-way electro-hydraulic proportional valve, a second two-position two-way electro-hydraulic proportional valve, a first pressure compensation valve and a first control oil way;
the oil inlet of the first two-position two-way proportional valve and the oil inlet of the first two-position two-way proportional valve are connected in parallel and communicated with a supply oil path P of a system, the oil outlet of the first two-position two-way proportional valve and the oil inlet of the first two-position two-way electrohydraulic proportional valve are connected in parallel at an output oil port A1 of the actuator, the oil outlet of the second two-position two-way proportional valve and the oil inlet of the second two-position two-way electrohydraulic proportional valve are connected in parallel at an output oil port B1 of the actuator, the oil outlet of the first two-position two-way electrohydraulic proportional valve and the oil outlet of the second two-position two-way electrohydraulic proportional valve are connected in parallel and communicated with the oil inlet of the first pressure compensation valve, and the oil outlet of the first pressure compensation valve is communicated with an oil return path T of the.
Furthermore, the first-connection control oil circuit comprises a first-connection two-position three-way reversing valve, a first-connection first two-position two-way reversing valve, a first-connection second two-position two-way reversing valve and a first-connection shuttle valve;
an oil outlet of the first-joint two-position three-way reversing valve is connected with an oil inlet of the first-joint two-position two-way reversing valve in parallel and is communicated with a first oil inlet of the first-joint shuttle valve, a second oil inlet of the first-joint shuttle valve is communicated with a control oil port K2 of the second-joint valve group, and an oil outlet of the first-joint shuttle valve is communicated with a control oil port K1 of the first-joint valve group;
an oil outlet of the first two-position two-way reversing valve in the first connection is communicated with a first control oil port of the pressure compensation valve in the first connection, a second control oil port of the pressure compensation valve in the first connection is communicated with an oil outlet of the second two-position two-way reversing valve in the first connection, and an oil inlet of the second two-position two-way reversing valve in the first connection is communicated with a load sensitive oil path LS of the system;
a control oil inlet of the first two-position two-way electro-hydraulic proportional valve and a first oil inlet of the first two-position three-way reversing valve are connected in parallel with an output oil port B1 of the actuator, a control oil inlet of the second two-position two-way electro-hydraulic proportional valve and a second oil inlet of the first two-position three-way reversing valve are connected in parallel with an output oil port A1 of the actuator, and a control oil outlet of the first two-position two-way electro-hydraulic proportional valve and a control oil outlet of the second two-position two-way electro-hydraulic proportional valve are connected in parallel with an oil return circuit T of the system.
Furthermore, the first-connection first two-position two-way electro-hydraulic proportional valve comprises an electro-hydraulic proportional valve pilot valve and an electro-hydraulic proportional valve main valve;
an oil inlet of a main valve of the electro-hydraulic proportional valve is communicated with an oil outlet of a first two-position two-way proportional valve, an oil outlet of the main valve of the electro-hydraulic proportional valve is communicated with an oil inlet of a first pressure compensation valve, a control oil inlet of the main valve of the electro-hydraulic proportional valve is communicated with an oil outlet of a pilot valve of the electro-hydraulic proportional valve, and a control oil outlet of the main valve of the electro-hydraulic proportional valve is communicated with an oil return path T;
an oil inlet of the electro-hydraulic proportional valve pilot valve is communicated with a first oil inlet of the one-connection two-position three-way reversing valve;
the first-connection second-position two-way electro-hydraulic proportional valve and the first-connection first-position two-way electro-hydraulic proportional valve are identical in structure.
Furthermore, in the multiple valve group, a second oil inlet of a first shuttle valve of the first valve group is communicated with an oil outlet of a second shuttle valve of the second valve group, a second oil inlet of the second shuttle valve of the second valve group is communicated with an oil outlet of a triple shuttle valve of the third valve group, and so on, a second oil inlet of an N-1 shuttle valve of an N-1 valve group is communicated with an oil outlet of an N-shuttle valve of an N-1 valve group, and a second oil inlet of the N-shuttle valve of the N-valve group is not communicated with any oil port.
Furthermore, the oil supply path P is connected to an output port of the variable displacement plunger pump, the oil return path T is connected to an oil tank, and a control oil port K1 of the first valve bank and the load-sensitive oil path LS are connected in parallel to an input end of a pump regulator of the variable displacement plunger pump.
The invention has the following beneficial effects:
1. the hydraulic oil return circuit load sensing system has a load sensing function, can greatly reduce energy waste caused by overhigh power of a hydraulic pump, has a function of independently controlling an oil way at an inlet and an outlet, has higher working efficiency and response performance, can greatly reduce the throttling loss of the oil return circuit load sensing system compared with the traditional oil return circuit load sensing system, and improves the effective rate of the whole energy of the system;
2. according to the invention, through independent control of the oil inlet and outlet paths, when a single actuator or a plurality of actuators work simultaneously and the sum of required flow is less than or equal to the flow of the pump, the electro-hydraulic proportional valve connected to the oil return path can adjust the flow area according to the oil inlet pressure of the actuator within a certain working range, so as to adjust the pressure of the oil outlet of the actuator; when the load changes, the pressure of the oil inlet of the actuator is basically kept unchanged by adjusting the pressure of the oil outlet of the actuator, and further the pressure difference between the oil inlet pressure of the actuator and the oil outlet pressure of the pump is kept unchanged, so that the flow of hydraulic oil entering the actuator is constant, the actuator can extend out or retract at a constant speed, and the working performance of the actuator is more stable;
3. according to the invention, the load sensitive system is compensated through the oil return path, when a plurality of actuators work simultaneously and the total required flow is larger than the flow of the pump, the system can equally distribute the flow to each actuator, instead of preferentially distributing the flow to the actuator with small load to enable the actuator with small load to move first, so that the problem that the actuators work asynchronously is effectively solved;
4. the invention has the function of preventing the actuator from falling too fast under the action of gravity to generate the suction phenomenon;
5. the hydraulic actuator has the advantages that the bidirectional action of the hydraulic actuator and the O, H, Y, C, K type multi-neutral-position functions can be controlled;
6. the combined valve has the advantages of simple design, convenient processing and good interchangeability, does not need to customize a corresponding valve core according to a determined hydraulic actuator, is easy to convert small-batch customized production into large-batch production, and has considerable economic value.
Drawings
FIG. 1 is a schematic diagram of a combination valve of the present invention having return compensating load sensing;
FIG. 2 is a schematic diagram of an application of the combination valve hydraulic system with return compensating load sensing of the present invention;
FIG. 3 is a schematic diagram of the one-way two-position two-way electro-hydraulic proportional valve;
FIG. 4 is a schematic diagram of the combination valve hydraulic system with return compensating load sensing of the present invention operating in a single actuator operating state;
FIG. 5 is a schematic diagram of the multi-actuator operation of the combination valve hydraulic system with the return compensating load sensing function in the flow unsaturated state according to the present invention;
fig. 6 is a working schematic diagram of the multi-actuator working under the flow unsaturated state of the combined valve hydraulic system with the return circuit compensation load sensing function of the invention.
In the figure: 1 a first valve group, 2 a first connection second two-position two-way electro-hydraulic proportional valve, 3 a connection first two-position two-way electro-hydraulic proportional valve, 4 a connection first two-position two-way proportional valve, 5 a connection second two-position two-way proportional valve, 6 a connection pressure compensation valve, 7 a connection second two-position two-way reversing valve, 8 a connection first two-position two-way reversing valve, 9 a connection two-position three-way reversing valve, 10 a connection shuttle valve, 11 a connection two-position three-way reversing valve, 12 a connection first two-position two-way reversing valve, 13 a connection first two-position electro-hydraulic proportional valve, 14 a connection second two-position two-electric hydraulic proportional valve, 15 a connection second two-position two-way proportional valve, 16 a connection first two-position two-way proportional valve, 17 a connection pressure compensation valve, 18 a connection second two-position two-way reversing valve, 19 a connection actuator, 20 a connection actuator, 21 an overflow valve, 22 variable plunger pump, 23 an oil tank, 24 electro-hydraulic, 25 electro-hydraulic proportional valve main valves, 26 two-way shuttle valves and 27 second-way valve groups.
Detailed Description
The following detailed description of the preferred embodiments of the present invention, taken in conjunction with the accompanying drawings, will make the advantages and features of the invention easier to understand by those skilled in the art, and thus will clearly and clearly define the scope of the invention.
Referring to fig. 1 to 3, a combination valve with a load-sensing function of oil return compensation includes a multi-valve set, a supply oil path P, An oil return path T, and a load-sensing oil path LS, where the multi-valve set shares a uniform supply oil path P, An oil return path T, and a load-sensing oil path LS, each multi-valve set has An output oil port An and An output oil port Bn connected to An actuator, and the multi-valve set includes a first multi-valve set 1, a second multi-valve set 27, a third multi-valve set … …, and An nth multi-valve set (none of the third to nth multi-valve sets is shown), where N is a natural number greater than or equal to 1. Each group valve has the same components and device composition and the same structural connection relation.
For convenience of description, the structure and operation of the present invention will be described in detail with reference to a two-valve set.
The first valve bank 1 comprises a first two-position two-way proportional valve 4, a second two-position two-way proportional valve 5, a first two-position two-way electro-hydraulic proportional valve 3, a second two-position two-way electro-hydraulic proportional valve 2, a pressure compensating valve 6 and a control oil circuit.
The oil inlet of the first two-position two-way proportional valve 4 and the oil inlet of the first two-position two-way proportional valve 5 are connected in parallel and communicated with a supply oil path P of a system, the oil outlet of the first two-position two-way proportional valve 4 and the oil inlet of the first two-position two-way electrohydraulic proportional valve 3 are connected in parallel at an output oil port A1 of the actuator, the oil outlet of the second two-position two-way proportional valve 5 and the oil inlet of the second two-position two-way electrohydraulic proportional valve 2 are connected in parallel at an output oil port B1 of the actuator, the oil outlet of the first two-position two-way electrohydraulic proportional valve 3 and the oil outlet of the second two-position two-way electrohydraulic proportional valve 2 are connected in parallel and communicated with the oil inlet of the first pressure compensating valve 6, and the oil outlet of the first pressure compensating valve 6 is communicated with an oil return path T of the.
Further, the one-connection control oil circuit comprises a one-connection two-position three-way reversing valve 9, a one-connection first two-position two-way reversing valve 8, a one-connection second two-position two-way reversing valve 7 and a one-connection shuttle valve 10.
An oil outlet of the first-joint two-position three-way reversing valve 9 is connected with an oil inlet of the first-joint two-position two-way reversing valve 8 in parallel and communicated with a first oil inlet of the first-joint shuttle valve 10, a second oil inlet of the first-joint shuttle valve 10 is communicated with a control oil port K2 of the second-joint valve group, and an oil outlet of the first-joint shuttle valve 10 is communicated with a control oil port K1 of the first-joint valve group.
An oil outlet of the first two-position two-way reversing valve 8 in the first connection is communicated with a first control oil port of the pressure compensation valve 6 in the first connection, a second control oil port of the pressure compensation valve 6 in the first connection is communicated with an oil outlet of the second two-position two-way reversing valve 7 in the first connection, and an oil inlet of the second two-position two-way reversing valve 7 in the first connection is communicated with a load sensitive oil path LS of the system.
The control oil inlet of the first two-position two-way electrohydraulic proportional valve 3 and the first oil inlet of the first two-position three-way reversing valve 9 are connected in parallel with the output oil port B1 of the actuator, the control oil inlet of the second two-position two-way electrohydraulic proportional valve 2 and the second oil inlet of the first two-position three-way reversing valve 9 are connected in parallel with the output oil port A1 of the actuator, and the control oil outlet of the first two-position two-way electrohydraulic proportional valve 3 and the control oil outlet of the second two-position two-way electrohydraulic proportional valve 2 are connected in parallel with the oil return circuit T of the system.
The second valve group 27 comprises a first two-position two-way proportional valve 16, a second two-position two-way proportional valve 15, a first two-position two-way electro-hydraulic proportional valve 13, a second two-position two-way electro-hydraulic proportional valve 14, a second pressure compensation valve 17 and a second control oil path. The two-way control oil circuit comprises a two-way two-position three-way reversing valve 11, a two-way first two-position two-way reversing valve 12, a two-way second two-position two-way reversing valve 18 and a two-way shuttle valve 26. Since the second valve combination 27 and the first valve combination 1 have the same components and device composition and the same structural connection relationship, the connection relationship between the components of the second valve combination 27 will not be described in detail here.
Further, the first two-position two-way electro-hydraulic proportional valve 3 comprises an electro-hydraulic proportional valve pilot valve 24 and an electro-hydraulic proportional valve main valve 25. Wherein, the electro-hydraulic proportional valve pilot valve 24 adopts a two-position two-way electromagnetic valve, and the electro-hydraulic proportional valve main valve 25 adopts a two-position two-way hydraulic control valve. As shown in fig. 3, an oil inlet of the electric hydraulic proportional valve main valve 25 is communicated with an oil outlet of the first two-position two-way proportional valve 4, an oil outlet of the electric hydraulic proportional valve main valve 25 is communicated with an oil inlet of the first pressure compensation valve 6, a control oil inlet of the electric hydraulic proportional valve main valve 25 is communicated with an oil outlet of the electric hydraulic proportional valve pilot valve 24, and a control oil outlet of the electric hydraulic proportional valve main valve 25 is communicated with the oil return path T. An oil inlet of the electro-hydraulic proportional valve pilot valve 24 is communicated with a first oil inlet of the one-connection two-position three-way reversing valve 9. For convenience of description, the pilot valve of the electro-hydraulic proportional valve is referred to as a pilot valve, and the main valve of the electro-hydraulic proportional valve is referred to as a main valve.
The first-connection second two-position two-way electro-hydraulic proportional valve 2 and the first-connection first two-position two-way electro-hydraulic proportional valve 3 are the same in structure, and are different from the first-connection second two-position two-way electro-hydraulic proportional valve 2 in that an oil inlet of an electro-hydraulic proportional valve main valve 25 is communicated with an oil outlet of a first-connection second two-position two-way proportional valve 5, and an oil inlet of an electro-hydraulic proportional valve pilot valve 24 is communicated with a second oil inlet of a first-connection two-position three-way reversing valve 9.
Further, in the multiple valve group, a second oil inlet of a first shuttle valve 10 of a first valve group 1 is communicated with an oil outlet of a second shuttle valve 26 of a second valve group 27, a second oil inlet of the second shuttle valve 26 of the second valve group 27 is communicated with an oil outlet of a third shuttle valve of a third valve group, and so on, a second oil inlet of an N-1 shuttle valve of an N-1 valve group is communicated with an oil outlet of an N-shuttle valve of an N-valve group, and a second oil inlet of the N-shuttle valve of the N-valve group is not communicated with any oil port.
The oil inlet of each valve group is connected with the output port of the variable plunger pump 22 through a supply oil path P, the oil return path T is connected with the oil tank 23, and a control oil port K1 and a load sensitive oil path LS of the first valve group 1 are connected in parallel with the input end of the pump regulator of the variable plunger pump 22.
The two-position two-way electro-hydraulic proportional valve in each valve group is uniformly controlled by a controller of a hydraulic system, when the working condition is determined, a certain control signal is manually and actively input according to the action requirement of a hydraulic actuator, and after the controller receives the signal, the controller sends a corresponding electric control signal to the pilot valve of the two-position two-way electro-hydraulic proportional valve of the corresponding linkage according to a corresponding control logic, so that the flow of hydraulic oil entering and flowing out of the pilot valve is controlled, and the purpose of controlling the main valve of the two-position two-way electro-hydraulic proportional valve is achieved. By controlling the position states of the two-position two-way electro-hydraulic proportional valves and the two-position two-way proportional valves in each valve group, the bidirectional action of the hydraulic actuator and various O, H, Y, C, K-type neutral position functions can be controlled.
In practical application, according to different working conditions, the two-way action of the hydraulic actuator is realized by combining different states by controlling the position states of the first two-position two-way proportional valve, the second two-position two-way proportional valve, the first two-position two-electrified hydraulic proportional valve, the second two-position two-electrified hydraulic proportional valve and the two-position three-way reversing valve of each valve group, as shown in table 1.
TABLE 1 list of implementation of actions of a sensory function combination valve actuator
According to different working conditions, the hydraulic system comprises three working modes: the system comprises a single-actuator working mode, a multi-actuator flow unsaturated working mode and a multi-actuator flow saturated working mode.
Specifically, when the system is in the single-actuator operating mode, the first valve group 1 is taken as an example, as shown in fig. 4. According to table 1, when a couple of actuators 19 is extended, a couple of first two-position two-way proportional valves 4 is opened, and a couple of second two-position two-way proportional valves 5 is closed; the opening pressure of a compression spring of the first two-position two-way electro-hydraulic proportional valve 3 and the second two-position two-way electro-hydraulic proportional valve 2 is preset to be P0, and P0 needs to be slightly higher than the load force. The pilot valve 24 of the first two-position two-way electro-hydraulic proportional valve 3 is controlled to be closed through the controller, the pilot valve 24 of the first two-position two-way electro-hydraulic proportional valve 2 is controlled to be opened, the left position of the first two-position three-way reversing valve is connected to a control oil way, the first two-position two-way reversing valve 8 is closed, and the second two-position two-way reversing valve 7 is closed; at this time, the pressures of the first control oil port and the second control oil port of the one-connection pressure compensation valve 6 are both 0, and the one-connection pressure compensation valve 6 is opened maximally under the action of the spring.
Further, the flow path of the hydraulic oil is as follows:
hydraulic oil flows out of the variable displacement plunger pump 22, flows into an oil inlet of the first two-position two-way proportional valve 4, flows out of an oil outlet of the first two-position two-way proportional valve 4, flows into a rodless cavity of the first actuator 19 from an output oil port A1 of the first actuator 19, and pushes a rod piece of the first actuator 19 to overcome load force and rod cavity pressure to extend out; the volume of the rod cavity is reduced, hydraulic oil flows out from a rod cavity output oil port B1 of the first-connection actuator 19, then flows into an oil inlet of the first-connection second two-position two-way electro-hydraulic proportional valve 2, flows out from an oil outlet of the first-connection second two-position two-way electro-hydraulic proportional valve 2, flows into an oil inlet of the first-connection pressure compensation valve 6, flows out from an outlet of the first-connection pressure compensation valve 6, and finally flows into the oil tank 23.
In the process, the hydraulic oil of the control oil path flows out from the rodless cavity oil pipe of the one-link actuator 19, the pressure of the hydraulic oil is the same as the pressure Pa of the rodless cavity output oil port A1 of the one-link actuator 19, the hydraulic oil flows into the control oil inlet of the main valve 25 of the electro-hydraulic proportional valve of the second two-position two-way electro-hydraulic proportional valve through the pilot valve 24 of the one-link second two-position two-way electro-hydraulic proportional valve 2, flows out from the control oil outlet of the main valve 25 and flows back to the oil tank 23. When the pressure Pa of the rodless cavity is greater than P0, the pressure difference pushes the valve core of the main valve 25 to move, so that the opening of the channel is increased, and the pressure of the rodless cavity is reduced; when the pressure of the rodless cavity and the compression force of the spring reach balance, the valve core of the main valve 25 of the one-connection two-position two-way electro-hydraulic proportional valve 2 stops moving.
Further, in the first-connection control oil path, the pressure of the hydraulic oil flowing out of the rodless cavity oil pipe of the first-connection actuator 19 is the same as the pressure Pa of the rodless cavity output oil port a1 of the first-connection actuator 19, the hydraulic oil flows into the second oil inlet of the first-connection two-position three-way reversing valve 9, flows out of the oil outlet of the first-connection two-position three-way reversing valve 9, flows into the first oil inlet of the first-connection shuttle valve 10, flows out of the oil outlet of the first-connection shuttle valve 10, flows out of the first-connection control oil port K1, flows into the variable displacement plunger pump 22 and acts on the pump regulator, so that the output displacement of the hydraulic pump is changed.
When the load force is suddenly increased to increase the rodless cavity pressure Pa of the one-link actuator 19, the hydraulic oil pressure of the control oil path is correspondingly increased, the hydraulic oil of the control oil path pushes the one-link second two-position two-way electro-hydraulic proportional valve 2 to move a compression spring leftwards, the flow area of the one-link second two-position two-way electro-hydraulic proportional valve 2 is increased, the pressure of the rod cavity is reduced, the rodless cavity pressure Pa is also reduced, and when the pressure of the control oil path and the spring compression force are balanced again, the one-link second two-position two-way electro-hydraulic proportional valve 2 stops moving, and the opening of a channel is not changed any more; when the load force is suddenly reduced to reduce the pressure Pa of the rodless cavity of the one-link actuator 19, the pressure of the control oil path is also reduced, the compression spring pushes the second two-position two-way electrohydraulic proportional valve 2 to move rightwards, the flow area of the second two-position two-way electrohydraulic proportional valve 2 is reduced, the pressure of the rod cavity is increased, the pressure Pa of the rodless cavity is also increased, and when the pressure of the control oil path and the compression force of the spring are balanced again, the second two-position two-way electrohydraulic proportional valve 2 stops moving.
From the above, the control oil circuit keeps the rodless chamber oil inlet pressure Pa in an interval near P0 all the time, and when the opening area of the first two-position two-way proportional valve 4 is not changed, the pressure Pp of the output port of the variable displacement plunger pump 22 is also basically not changed, which is expressed by the formula
It can be known that, at this time, the flow rate of the hydraulic oil passing through the first two-position two-way proportional valve 4 in one set is basically kept unchanged, and then the extension speed of the actuator 19 in one set is constant, and the extension speed is not affected by the load change.
The pressure of the hydraulic oil in the control oil way is the same as that of the rodless cavity, and the utilization rate of the output power of the engine is improved by adjusting the displacement of the variable plunger pump 22. The flow of an oil inlet path and an oil outlet path is adjusted through a first two-position two-way proportional valve 4 connected with an inlet and outlet independent system, the pressure of the oil inlet path and the oil outlet path is adjusted through a second two-position two-way electro-hydraulic proportional valve 2 connected with a second two-position two-way proportional valve, so that the opening area of the second two-position two-way electro-hydraulic proportional valve 2 connected with the first two-position two-way electro-hydraulic proportional valve can be changed according to the pressure change of the oil inlet path, the pressure of the oil inlet path is adjusted, the pressure of the oil inlet path tends to be stable, the action of an actuator 19 connected with the first two-position two-way electro-hydraulic proportional valve is.
Specifically, when the system is in the multi-actuator flow unsaturated operation mode, the operation principle is as shown in fig. 5. The working principle of this working mode is explained in detail by taking the first and second valve block 1, 27 as an example according to table 1.
When the first two-position two-way proportional valve 4 and the second two-position two-way proportional valve 5 are simultaneously extended, the first two-position two-way proportional valve 19 and the second two-position two-way proportional valve 20 are opened; the opening pressure of a compression spring of the first-connection second-position two-way electro-hydraulic proportional valve 2 and the first-connection first-position two-way electro-hydraulic proportional valve 3 is preset to be P1, and P1 needs to be slightly higher than the load force of the first-connection actuator 19. The pilot valve 24 of the first two-position two-way electro-hydraulic proportional valve 3 in the first connection is controlled to be closed through the controller, the pilot valve 24 of the second two-position two-way electro-hydraulic proportional valve 3 in the first connection is controlled to be opened, the left position of the first two-position three-way reversing valve 9 in the first connection is connected to a control oil way, the first two-position two-way reversing valve 8 in the first connection is closed, and the second two-position two-way reversing valve 7 in the first connection is closed; at this time, the pressures of the first control oil port and the second control oil port of the one-connection pressure compensation valve 6 are both 0, and the one-connection pressure compensation valve 6 is opened maximally under the action of the spring.
Meanwhile, the two-way first two-position two-way proportional valve 16 is opened, and the two-way second two-position two-way proportional valve 15 is closed; the opening pressure of a compression spring of the two-way first two-position two-way electro-hydraulic proportional valve 13 and the two-way second two-position two-way electro-hydraulic proportional valve 14 is preset to be P2, and P2 needs to be slightly higher than the load force of the two-way actuator 20. The pilot valve 24 of the duplex first two-position two-way electro-hydraulic proportional valve 13 is controlled to be closed through the controller, and the pilot valve 24 of the duplex second electro-hydraulic proportional valve 14 is controlled to be opened; the left position of the two-way two-position three-way reversing valve 11 is connected into a control oil circuit, the two-way first two-position two-way reversing valve 12 is closed, and the two-way second two-position two-way reversing valve 18 is closed; at this time, the pressures of the first control oil port and the second control oil port of the duplex pressure compensation valve 17 are both 0, and the duplex pressure compensation valve 17 is opened maximally under the action of the spring.
In this operating mode, the hydraulic oil flow path and the pressure adjustment process in the respective valve groups of the first and second valve group 1 and 27 are the same as those in the single actuator operating mode described above, and details thereof are not described here.
Except that in this mode of operation: in the first-connection control oil path, the pressure Pa of hydraulic oil flowing out of a rodless cavity oil pipe of the first-connection actuator 19 is the same as the pressure at the rodless cavity oil pipe of the first-connection actuator 19, the hydraulic oil flows into a second oil inlet of the first-connection two-position three-way reversing valve 9, flows out of an oil outlet of the first-connection two-position three-way reversing valve 9 and flows into a first oil inlet of the first-connection shuttle valve 10; in the double-control oil path, the pressure Pb of the hydraulic oil flowing out of the rodless cavity oil pipe of the double-actuator 20 is the same as the pressure at the rodless cavity oil pipe of the double-actuator 20, and flows into the second oil inlet of the double-two-position three-way reversing valve 11, flows out of the oil outlet of the double-two-position three-way reversing valve 11, flows into the first oil inlet of the second shuttle valve 26, flows out of the oil outlet of the second shuttle valve 26, then flows out of the double-control oil port K2, and then flows into the second oil inlet (shown as a port K1') of the first shuttle valve 10.
When the pressure difference exists between the hydraulic oil pressure in the first oil inlet and the hydraulic oil pressure in the second oil inlet of the shuttle valve 10, the valve core of the shuttle valve 10 is pushed by the pressure difference to block the oil inlet with lower pressure, and then the oil inlet with higher pressure of the hydraulic oil in the control oil path is opened. The hydraulic oil flows out from the oil outlet of the shuttle valve 10, the pressure Pmax of the hydraulic oil is the larger value of the first inlet pressure Pa and the second inlet pressure Pb, and then the hydraulic oil flows out from the control oil port K1, flows into the variable displacement plunger pump 22 and acts on the pump regulator, so that the output displacement of the hydraulic pump is changed.
The control oil circuit enables the inlet pressure Pa of the one-link rodless cavity to be always maintained in an interval near P1, enables the inlet pressure Pb of the two-link rodless cavity to be always maintained in an interval near P2, and when the opening area of the one-link first two-position two-way proportional valve 4 and the opening area of the two-link first two-position two-way proportional valve 16 are not changed, the outlet pressure Pp of the variable plunger pump is basically not changed.
As can be seen from the above formula (1), at this time, the flow rate Q1 of the hydraulic oil passing through the first two-position two-way proportional valve 4 and the flow rate Q2 of the hydraulic oil passing through the first two-position two-way proportional valve 16 in a unit time are substantially constant, the rod extending speed V1 of the first two-position actuator 19 and the rod extending speed V2 of the second two-position actuator 20 are both constant and are not affected by load changes, and the rod extending speed V1 of the first two-position actuator 19 and the rod extending speed V2 of the second two-position actuator 20 can be set or changed by adjusting the flow area S1 of the first two-position two-way proportional valve 4 and the flow area S2 of the first two-position two-way proportional valve 16.
Specifically, when the system is in the multi-actuator flow saturation operating mode, the operating principle is as shown in fig. 6. The working principle of this working mode is explained in detail by taking the first and second valve block 1, 27 as an example according to table 1.
When the first two-position two-way proportional valve 4 and the second two-position two-way proportional valve 5 are simultaneously extended, the first two-position two-way proportional valve 19 and the second two-position two-way proportional valve 20 are opened; the opening pressure of a first-connection second two-position two-way electro-hydraulic proportional valve 2 and a first-connection first two-position two-way electro-hydraulic proportional valve 3 is preset to be 0, a pilot valve 24 of the first-connection first two-position two-way electro-hydraulic proportional valve 3 is controlled to be closed through a controller, and the pilot valve 24 of the first-connection second two-position two-way electro-hydraulic proportional valve 2 is opened; the left position of the one-connection two-position three-way reversing valve 9 is connected to a control oil path, the one-connection first two-position two-way reversing valve 8 is opened, and the one-connection second two-position two-way reversing valve is opened 7.
Meanwhile, the two-way first two-position two-way proportional valve 16 is opened, and the two-way second two-position two-way proportional valve 15 is closed; the opening pressure of the two-way first two-position two-way electro-hydraulic proportional valve 13 and the two-way second two-position two-way electro-hydraulic proportional valve 14 is preset to be 0. The pilot valve 24 of the two-way first two-position two-way electro-hydraulic proportional valve 13 is controlled to be closed through the controller, and the pilot valve 24 of the two-way second two-position two-way electro-hydraulic proportional valve 14 is controlled to be opened; the left position of the two-way two-position three-way reversing valve 11 is connected into a control oil circuit, the two-way first two-position two-way reversing valve 12 is opened, and the two-way second two-position two-way reversing valve 18 is opened.
In this working mode, the hydraulic oil flow path in each valve group of the first valve group 1 and the second valve group 27 and the displacement adjustment process of the variable displacement plunger pump 22 are the same as those in the above-mentioned multiple actuator flow unsaturated working mode, and details are not described here.
Except that in this mode of operation: because the preset pressure of the spring of the first two-position two-way electro-hydraulic proportional valve 2 is 0, the hydraulic oil flowing out of the oil outlet of the first two-position two-way proportional valve 4 directly pushes the valve core of the second two-position two-way electro-hydraulic proportional valve 2 to open the valve port of the main valve to the maximum, and therefore, no redundant throttling loss exists in an oil return path. Hydraulic oil flowing out of an oil outlet of the one-connection two-position three-way reversing valve 9 with pressure Pa flows into an oil inlet of the one-connection first two-position two-way reversing valve 8, flows out of an oil outlet of the one-connection first two-position two-way reversing valve 8 and then flows into a first control oil inlet of the one-connection pressure compensation valve 6; and the pressure Pmax of the hydraulic oil flowing out from the K1 port is the larger pressure value between the first oil inlet of the one-way shuttle valve 10 and the second oil inlet of the one-way shuttle valve 10, then the hydraulic oil flows into the one-way load sensitive oil path LS, then the hydraulic oil flows into the oil inlet of the one-way second two-position two-way reversing valve 7, flows out of the oil outlet of the one-way second two-position two-way reversing valve 7 and finally flows into the second control oil port of the one-way pressure compensation valve 6.
When the hydraulic oil pressure Pa of a first control oil port of the one-connection pressure compensation valve 6 is equal to the pressure Pmax of a second control oil port, the one-connection pressure compensation valve 6 is completely opened, and the flow area is the largest; when the hydraulic oil pressure Pa of the first control oil port of the one-connection pressure compensation valve 6 is smaller than the pressure Pmax of the second control oil port, the valve core of the one-connection pressure compensation valve 6 moves towards one side of the first control oil port and compresses the spring, and the valve port through-flow area of the one-connection pressure compensation valve 6 is reduced. At this time, the flow area is decreased to increase the rod chamber pressure of the one-way actuator 19, and thus the rodless chamber pressure Pa, and when the first control port hydraulic oil pressure and the second control port pressure differential pressure (Pmax-Pa) of the one-way pressure compensation valve 6 are equal to the spring acting force Pk, the spool of the one-way pressure compensation valve 6 stops moving. Pk is negligible compared to Pa, Pa is approximately equal to Pmax when the pressure compensation valve 6 stops moving.
Furthermore, as the preset pressure of the spring of the two-way second two-position two-way electro-hydraulic proportional valve 14 is 0, the hydraulic oil flowing out of the oil outlet of the two-way first two-position two-way proportional valve 16 directly pushes the valve core of the second two-position two-way electro-hydraulic proportional valve 2 to open the valve port of the main valve to the maximum, and therefore, no redundant throttling loss exists in the oil return path. Hydraulic oil flowing out of an oil outlet of the two-way two-position three-way reversing valve 11 with the pressure of Pb flows into an oil inlet of the two-way first two-position two-way reversing valve 12, flows out of an oil outlet of the two-way first two-position two-way reversing valve 12 and then flows into a first control oil port of the two-way pressure compensation valve 17; the hydraulic oil which flows into a load-sensitive oil line LS from a control oil port K1 and has a pressure Pmax flows into an oil inlet of the second two-position two-way reversing valve 18, flows out of an oil outlet of the second two-position two-way reversing valve 18 and finally flows into a second control oil port of the pressure compensation valve 17.
When the hydraulic oil pressure Pb of the first control oil port of the duplex pressure compensation valve 17 is equal to the pressure Pmax of the second control oil port, the duplex pressure compensation valve 17 is completely opened, and the flow area is the largest; when the hydraulic oil pressure Pb at the first control oil port of the two-way pressure compensation valve 17 is smaller than the pressure Pmax at the second control oil port, the valve core of the two-way pressure compensation valve 17 moves towards one side of the first control oil port and compresses the spring, and the valve port flow area of the two-way pressure compensation valve 17 is reduced. At this time, the flow area decreases to increase the rod chamber pressure of the double actuator 20 and thus the rod chamber pressure Pb, and when the first control port hydraulic oil pressure and the second control port pressure differential pressure (Pmax-Pb) of the double pressure compensation valve 17 become equal to the spring force Pk, the spool of the double pressure compensation valve 17 stops moving. Pk is negligible compared to Pb, and Pb is approximately equal to Pmax when dual pressure compensating valve 17 stops moving.
The low load loop and the return oil pressure are improved due to the throttling compensation effect of the pressure compensation valve on the return oil path, so that the pressure of the rodless cavities of the first link valve, the second link valve, the … and the Nth link valve is equal to Pmax, the pressure difference between the front and the back of each first two-position two-way proportional valve is equal, and the flow formula passing through the valve port is obtained by the formula
Therefore, at the moment, the flow distribution of each executing element is only related to the opening area of each first two-position two-way proportional valve, but not flows to the actuator with small load, so that the actuator with small load moves first, the problem that the actuator does not work synchronously is solved, the flow saturation resistance function is realized, and the actuators of all the valves can move synchronously.
The inlet and outlet independent control system is adopted, when the opening area of each first two-position two-way proportional valve is changed to adjust the flow distribution on the oil inlet passage, the second two-position two-way electro-hydraulic proportional valve on the oil return passage is completely opened, no redundant throttling loss is caused, and compared with a traditional oil return passage load sensitive system in which an oil inlet throttling edge and an oil return throttling edge are throttled simultaneously, the energy utilization rate of the system is greatly improved.
The invention also has the advantage of preventing the actuator from falling too fast under the action of gravity to generate a suction phenomenon. The specific realization principle is as follows: when the system is in a single-actuator working condition or a multi-actuator flow unsaturated working condition, and when one coupled valve actuator descends under the action of gravity, the system can prevent the actuator from descending too fast by reducing the flow area of the electric hydraulic proportional valve of the oil return path and increasing the pressure of the oil return path, so that the suction phenomenon is prevented; when the system is in a multi-actuator flow saturation working condition and an actuator of a certain linkage valve descends under the action of gravity, the system can prevent the actuator from descending too fast by reducing the flow area of the oil return path pressure compensation valve and increasing the oil return path pressure, so that the phenomenon of air suction is prevented.
According to different working conditions and actuators, the system can realize O, H, Y, C, K type multiple neutral functions by combining different position states according to the position states of the first two-position two-way proportional valve, the second two-position two-way proportional valve, the first two-position two-electrified hydraulic proportional valve and the second two-position two-electrified hydraulic proportional valve which are controlled to be connected in series, as shown in table 2.
TABLE 2 list of the function realizations of the middle positions of the combination valve with the load-sensitive function with the independent control of the outlet oil path
The above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications of equivalent structures and equivalent processes performed by the present specification and drawings, or directly or indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (5)
1. The utility model provides a combination valve with sensitive function of return oil circuit compensation load, includes the manifold block, supplies with oil circuit P, return oil circuit T, the sensitive oil circuit LS of load, the manifold block is public unified supplies with oil circuit P, return oil circuit T and the sensitive oil circuit LS of load, and each manifold block all has output oil port An, the output oil port Bn that links to each other with the executor, its characterized in that: the multi-connection valve group comprises a first connection valve group, a second connection valve group, a third connection valve group and … …, wherein N is a natural number more than or equal to 1;
each valve group has the same components and device composition and the same structural connection relationship;
the first valve bank comprises a first two-position two-way proportional valve, a second two-position two-way proportional valve, a first two-position two-way electro-hydraulic proportional valve, a second two-position two-way electro-hydraulic proportional valve, a first pressure compensation valve and a first control oil way;
the oil inlet of the first two-position two-way proportional valve and the oil inlet of the first two-position two-way proportional valve are connected in parallel and communicated with a supply oil path P of a system, the oil outlet of the first two-position two-way proportional valve and the oil inlet of the first two-position two-way electrohydraulic proportional valve are connected in parallel at an output oil port A1 of the actuator, the oil outlet of the second two-position two-way proportional valve and the oil inlet of the second two-position two-way electrohydraulic proportional valve are connected in parallel at an output oil port B1 of the actuator, the oil outlet of the first two-position two-way electrohydraulic proportional valve and the oil outlet of the second two-position two-way electrohydraulic proportional valve are connected in parallel and communicated with the oil inlet of the first pressure compensation valve, and the oil outlet of the first pressure compensation valve is communicated with an oil return path T of the.
2. A combination valve with return compensation load sensing as claimed in claim 1 wherein: the first-connection control oil circuit comprises a first-connection two-position three-way reversing valve, a first-connection two-position two-way reversing valve, a second-connection two-position two-way reversing valve and a shuttle valve;
an oil outlet of the first-joint two-position three-way reversing valve is connected with an oil inlet of the first-joint two-position two-way reversing valve in parallel and is communicated with a first oil inlet of the first-joint shuttle valve, a second oil inlet of the first-joint shuttle valve is communicated with a control oil port K2 of the second-joint valve group, and an oil outlet of the first-joint shuttle valve is communicated with a control oil port K1 of the first-joint valve group;
an oil outlet of the first two-position two-way reversing valve in the first connection is communicated with a first control oil port of the pressure compensation valve in the first connection, a second control oil port of the pressure compensation valve in the first connection is communicated with an oil outlet of the second two-position two-way reversing valve in the first connection, and an oil inlet of the second two-position two-way reversing valve in the first connection is communicated with a load sensitive oil path LS of the system;
a control oil inlet of the first two-position two-way electro-hydraulic proportional valve and a first oil inlet of the first two-position three-way reversing valve are connected in parallel with an output oil port B1 of the actuator, a control oil inlet of the second two-position two-way electro-hydraulic proportional valve and a second oil inlet of the first two-position three-way reversing valve are connected in parallel with an output oil port A1 of the actuator, and a control oil outlet of the first two-position two-way electro-hydraulic proportional valve and a control oil outlet of the second two-position two-way electro-hydraulic proportional valve are connected in parallel with an oil return circuit T of the system.
3. A combination valve with return compensation load sensing as claimed in claim 2 wherein: the first-connection first two-position two-way electro-hydraulic proportional valve comprises an electro-hydraulic proportional valve pilot valve and an electro-hydraulic proportional valve main valve;
an oil inlet of a main valve of the electro-hydraulic proportional valve is communicated with an oil outlet of a first two-position two-way proportional valve, an oil outlet of the main valve of the electro-hydraulic proportional valve is communicated with an oil inlet of a first pressure compensation valve, a control oil inlet of the main valve of the electro-hydraulic proportional valve is communicated with an oil outlet of a pilot valve of the electro-hydraulic proportional valve, and a control oil outlet of the main valve of the electro-hydraulic proportional valve is communicated with an oil return path T;
an oil inlet of the electro-hydraulic proportional valve pilot valve is communicated with a first oil inlet of the one-connection two-position three-way reversing valve;
the first-connection second-position two-way electro-hydraulic proportional valve and the first-connection first-position two-way electro-hydraulic proportional valve are identical in structure.
4. A combination valve with return compensation load sensing as claimed in claim 2 wherein: in the multi-connection valve group, a second oil inlet of a first connection shuttle valve of the first connection valve group is communicated with an oil outlet of a second connection shuttle valve of the second connection valve group, a second oil inlet of a second connection shuttle valve of the second connection valve group is communicated with an oil outlet of a third connection shuttle valve of the third connection valve group, and the like, and a second oil inlet of an N-1 connection shuttle valve of the N-1 connection valve group is communicated with an oil outlet of an N connection shuttle valve of the N-1 connection valve group.
5. A combination valve with return compensation load sensing as claimed in claim 2 wherein: the oil supply path P is connected with an output port of the variable plunger pump, the oil return path T is connected with an oil tank, and a control oil port K1 and a load sensitive oil path LS of the first valve bank are connected in parallel with an input end of a pump regulator of the variable plunger pump.
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| CN111577689A (en) * | 2020-06-03 | 2020-08-25 | 江苏科迈液压控制系统有限公司 | Flow saturation resisting method for load sensitive proportional multi-way valve |
| CN111734877A (en) * | 2020-07-09 | 2020-10-02 | 四川航天烽火伺服控制技术有限公司 | Ball valve actuator |
| CN112648244A (en) * | 2021-02-19 | 2021-04-13 | 太原理工大学 | Pump-valve-cooperated multi-actuator electro-hydraulic system and control method thereof |
| CN113107929A (en) * | 2021-04-15 | 2021-07-13 | 中国铁建重工集团股份有限公司 | Load-sensitive hydraulic circuit |
| CN115681262A (en) * | 2022-10-27 | 2023-02-03 | 华东交通大学 | Load-sensitive electro-hydraulic conversion oil inlet module |
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